US4520863A - Heat-exchanger with a bundle of parallelly extending pipes adapted to be acted upon by air - Google Patents

Heat-exchanger with a bundle of parallelly extending pipes adapted to be acted upon by air Download PDF

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Publication number
US4520863A
US4520863A US06/436,937 US43693782A US4520863A US 4520863 A US4520863 A US 4520863A US 43693782 A US43693782 A US 43693782A US 4520863 A US4520863 A US 4520863A
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United States
Prior art keywords
heat
exchanger
pipe
exchanger plate
bundle
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Expired - Fee Related
Application number
US06/436,937
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English (en)
Inventor
Rudolf Andres
Helmut Grantz
Wolf-Dietrich Munzel
Wolfgang Odebrecht
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Daimler Benz AG
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Daimler Benz AG
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Assigned to DIAMLER-BENZ AKTIENGESELLSCHAFT reassignment DIAMLER-BENZ AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: ANDRES, RUDOLF, GRANTZ, HELMUT, MUNZEL, WOLF-DIETRICH, ODEBRECHT, WOLFGANG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0246—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid heat-exchange elements having several adjacent conduits forming a whole, e.g. blocks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0233—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes the conduits having a particular shape, e.g. non-circular cross-section, annular

Definitions

  • the present invention relates to a heat-exchanger with a bundle of general parallelly extending pipes adapted to be acted upon by air.
  • a heat exchanger of this same general type is disclosed, for example, in the non-prepublished German Offenlegungsschrift No. 30 31 624.
  • the heat-exchanger illustrated in the above-noted Offenlegungschrift serves selectively for the cooling or for the heating of the passenger space of a motor vehicle.
  • different heat-exchanger heads are provided, of which one is adapted to be acted upon with hot water for heating and the other with a cooling medium for cooling.
  • the distribution of the supplied heat, respectively, of the cooling output onto the air stream takes place by the pipe bundle whose pipes are constructed as so-called heatpipes of conventional construction.
  • Similar arrangements of a heat-exchanger selectively utilizable both for cooling and for heating are disclosed in the German Offenlegungsschrift 27 56 119 and in the German Offenlegungsschrift No. 28 00 265.
  • a principal object of the present invention resides in the construction of a heat-exchanger which can be manufactured in a rational manner and of which a good heat transfer can be expected between the heat carrier medium and the heat-pipes.
  • the underlying problems are solved according to the present invention in that the pipes and heat-pipe hollow spaces of a pipe row are in the form of a first uniform heat-exchanger plate extending into the air stream and up to the area of the heat-exchanger head.
  • the pipes of the heat-exchanger include channels formed into the heat-exchanger plate, and the heat-exchanger plates are arranged parallelly to the air stream.
  • a further heat-exchanger plate limited to the heat-exchanger head and containing heat carrier channels is coordinated to each first heat-exchanger plate, whereby adjacent heat-exchanger plates are brazed to one another in a heat-conducting manner.
  • two mutually separate channel systems can be established within a narrow space, whereby owing to the brazing of the heat-exchanger plates, the two channel systems are intimately connected with each other in a heat conducting manner.
  • the two channel systems which are in heat-exchanging relationship can be manufactured in a rational and price-favorable manner. By reason of a tight packing of many mutually adjoining channels, a good heat-exchange can be adduced in a small space.
  • the heat-exchanger plates may be constructed as extruded profiles or also as partial composite laminated bodies.
  • FIG. 1 is an elevational view in the direction of the air stream of a first embodiment of a heat-exchanger according to the present invention, with heat-exchanger plates constructed as extruded profiles;
  • FIG. 2 is a top plan view of the heat-exchanger illustrated in FIG. 1;
  • FIG. 3 is a partial cross-sectional view through the heat-exchanger according to FIG. 1, on an enlarged scale compared to FIGS. 1 and 2;
  • FIG. 4 is a cross-sectional view taken along line IV--IV of the heat-exchanger according to FIG. 3, through the part of a heat-exchanger plate acted upon by air;
  • FIG. 5 is an elevational view, also in the direction of the air stream, of a further embodiment of a heat-exchanger according to the present invention with heat-exchanger plates constructed as partial composite laminated bodies;
  • FIG. 6 is a partial section, on an enlarged scale, of the heat-exchanger of FIG. 5;
  • FIG. 7 is a side elevation view of the heat-exchanger shown in FIG. 5;
  • FIG. 8 is an elevational view of a further embodiment of a heat-exchanger according to the present invention with partial composite laminated bodies as heat-exchanger plates and with subdivision of the heat-exchanger heads into sections for drying the treated air.
  • heat-exchangers generally designated by reference numeral 1, 1', 1" and 1'" illustrated in the different figures, essentially include an upper heat-exchanger head 4, respectively, 4', of a pipe bundle 2, respectively, 2' acted upon by air, with the air stream indicated by reference numeral 3, and of a lower heat-exchanger head 5, respectively, 5'.
  • the individual pipes of the pipe bundle 2 and 2' are designated by reference numerals 6 and 6'.
  • the heat-exchangers are formed by two different types of heat-exchanger plates, of which one type extends over the entire height of the heat-exchanger, whereas the other type of the heat-exchanger plates is limited to the respective heat-exchanger head.
  • the first type of the heat-exchanger plate 8, 8', 8" and 8'" includes the pipes 6 and 6' and the heat-pipe hollow spaces 7 and 7' of the pipe bundle, respectively, of the pipe rows.
  • These heat-exchanger plates 8, 8', 8" and 8'" extend parallel to the air stream 3 and continue beyond the air stream up the area of the respective heat-exchanger head.
  • the two types of the heat-exchanger plates 8 and 9 are constructed in the form of a board-shaped extruded profile which contains several parallel channels extending adjacent one another.
  • the heat-exchanger plates extending cross-wise to one another inside of the heat-exchanger head are brazed together over the entire extent of the heat-exchanger head and form a compact block, so to speak of.
  • the extruded profiles have in cross section the shape of a ladder and form several rectangular or square channels which represent the pipes.
  • the part of the pipes acted upon by air is provided with heat-transfer ribs or fins which in the embodiment according to FIGS. 1 to 4 are in the form of erected curved ribs 11 peeled shaving-like out of the outer wall.
  • the extrusion profiles forming the heat carrier channels 9 are connected with each other by connecting profiles 16 extending transversely thereto, which in cross section have the same shape as the extruded profiles of the heat-exchanger head shown in cross section in FIG. 3.
  • the connecting profiles 16 are provided at the inlet openings of the extrusion profiles of the heat-exchanger plates extending through the heat-exchanger head.
  • the heat-exchanger plates include a groove which, in its width, corresponds to the profile thickness and which intersects the channels of the connecting profiles.
  • the connecting profile prepared in such a manner is mounted over the projecting ends of the heat-exchanger plates under interposition of a so-called soldering or brazing mask at the respective contact places and is sealingly brazed thereto in one operation together with the other brazed connections.
  • One of the end faces of the connecting profile 16 is closed whereas the opposite side of the same connecting profile is provided with an inlet, respectively, with a discharge or outlet connection.
  • the heat-exchanger plates 8 are connected with each other by transversely extending connecting profiles 14.
  • a connection of the channels 9 for a through-flow of a heat carrier medium is indispensable and functionally necessary
  • a corresponding cross connection of the heat-pipe hollow spaces 7 of the individual heat-exchanger plates 8 is not necessarily required.
  • the temperature level transversely to the air stream is compensated by a cross connection of the heat-pipe hollow spaces disposed adjacent one another in the air stream.
  • Transversely extending grooves 17 are also provided in the connecting profile 14 for the heat-exchanger plates 8, which grooves correspond to the profile thickness and which intersect the channels inside of the extrusion profile 14.
  • the connecting profile 14 does not require any individual channels but could represent a rectangular flat pipe. A subdivision into channels which corresponds exactly to the cross section illustrated in FIG. 4, however, is appropriate for reasons of rigidity. Additionally, a separation of the individual pipes inside of the heat-exchanger plates is achieved by an identical subdivision of the connecting profile 14 as with the heat-exchanger plates 8.
  • the pipes which lie at different depths inside of the heat-exchanger--as viewed in the air flow direction-- can be adjusted individually to different operating points by reason of different fillings so that the tendency of a temperature gradient decreasing in the air flow direction between air, respectively, and the heat-exchanger can be compensated thereby and the heat transfer capacity can be optimized.
  • the heat-exchanger plates 8' and 9' are constructed as two-layer partial composite laminated bodies. One side each of the partial composite laminated body is constructed flat and plane; thus, two heat-exchanger plates are brazed together by means of this side completely so that a heat contact with good heat conducting properties and of large area in cross section results between the two.
  • the first heat-exchanger plates 8' which are disposed parallel adjacent one another in the air stream are connected with each other by connecting pipes 13 so that transversely to the air stream all pipes of the bundle 2' possess the same operating point. As shown by the embodiment according to FIG.
  • the pipes can be combined groupwise in the air flow direction in such a manner that the individual groups of heat-pipe hollow spaces disposed one behind the other in the air flow direction do not have any connection with each other.
  • Groups of heat-pipe hollow spaces which are disposed at the same depth in the air flow direction, are connected with each other transversely to the air stream by way of connecting pipes 13.
  • the heat-exchanger plates 10' and 10" are connected transversely with each other on the inlet side and on the outlet side so that they are adapted to be traversed parallel to one another by a heat carrier medium.
  • the heat carrier channels 9', respectively, 9" formed within the same, extend appropriately without branching in a manner wherein they meander over the extent of the heat-exchanger plate whereby channel sections of the heat-exchanger channel are disposed congruent with channel sections of the heat-pipe hollow spaces in the heat-exchanger plates 8', respectively, 8" over as large as possible a length.
  • the heat-pipe hollow spaces of the heat-exchanger plates 8', respectively, 8" are constructed approximately ladder-shaped within the area of the heat-exchanger heads whereby the channel sections corresponding to the rungs of this ladder are disposed congruent with channel sections of the heat-carrier channels. As a result thereof, short heat transfer paths from one type of channel to the other type of channel are achieved.
  • the connecting pipes 15 for the further heat-exchanger plates 10', respectively, 10" are secured in quite a similar manner as the connecting pipes 13 for the first heat-exchanger plates.
  • the transversely extending pipes and the edge of the partial composite laminated bodies are milled-in at the respective inlet places in such a manner that openings with approximately congruent spatial configuration of the boundary contour result.
  • the parts are sealingly brazed to one another by interposition of a corresponding soldering mask and by placing the same one on the other and by clamping fast the connecting pipe.
  • the heat transfer is improved by heat transfer ribs at the part of the heat-exchanger plates acted upon by air.
  • the heat transfer ribs are formed in the shape of transversely projecting tongues or fins 12 which are displaced out of wall portions of the heat-exchanger plates, and the wall portions disposed between the pipes are utilized for this purpose.
  • FIG. 8 The further embodiment of a heat-exchanger generally designated by reference numeral 1'" illustrated in FIG. 8 is characterized essentially in that the two heat-exchanger heads are subdivided into two sections 18 and 19 disposed one behind the other in the direction of the air flow.
  • the upper heat-exchanger head is adapted to be acted upon with a tempered heat carrier medium colder than the dew point temperature of the acted-upon air, for example, with a liquid cooling medium
  • the lower heat-exchanger head is adapted to be traversed by a tempered heat carrier medium, for example, by heating water tempered warmer than room temperature.
  • the heat-exchanger heads Owing to the subdivision of the heat-exchanger heads into two sections disposed one behind the other, these sections can be turned off individually so that only one of the sections and correspondingly the associated part of the pipe bundle can be acted upon by itself in an isolated manner.
  • Such a construction of the heat-exchanger, respectively, of the heat-exchanger heads is purposeful for the drying of humid air.
  • the three first pipes of the pipe rows disposed in the air stream are cooled in that cooling medium is supplied to the upper heat-exchanger head whereby the rear section of this heat-exchanger head is turned off and correspondingly the three rear pipe rows are not cooled.
  • the lower heat-exchanger head is acted upon with heating water whereby in that case the forward section is rendered inoperative and only the rear pipes of the pipe rows are heated.
  • the humidity can be removed from the air supplied through the heat-exchanger in that the moisture condenses at the forward cold pipes; subsequently, the cooled-off air is again heated to normal temperature at the rear pipes so that the dried air, respectively, is retained at normal temperature.
  • the heating water supply is turned off and instead cooling medium to be evaporated is conducted through the upper heat-exchanger head.
  • the medium disposed in the heat pipe hollow spaces is evaporated in the pipes of the bundle exposed to the air stream whereby heat is removed from the air.
  • the evaporated medium rises on the inside of the pipes and condenses in the sections of the heat pipe hollow spaces disposed in the upper heat-exchanger head, whereby the absorbed heat is transferred to the cooling medium and the latter evaporates.
  • the formed condensate runs back downwardly into the part of the heat pipe hollow spaces which are exposed to the air stream by gravitational influence and/or by capillary action on the pipe inside, as a result of which the circulation again also closes.
  • the condensation portion of the heat pipe hollow space is arranged above the evaporating portion as viewed in the gravitational direction so that a condensate return flow is favored by gravitational influence. This has a favorable influence on a high capacity heat transfer.
  • Partial composite laminate bodies or structures are such structures, also known as so-called "Roll-Bond” plates or structures, which consist, for example, of a corresponding number of aluminum plates that are imprinted with a separating substance at those places where the plates are intended to form hollow spaces and are subsequently rolled together, one lying upon the other, as a result of which the plates are intimately welded together by the rolling pressure and the materials deformation at the non-imprinted places.
  • Roll-Bond plates or structures consist, for example, of a corresponding number of aluminum plates that are imprinted with a separating substance at those places where the plates are intended to form hollow spaces and are subsequently rolled together, one lying upon the other, as a result of which the plates are intimately welded together by the rolling pressure and the materials deformation at the non-imprinted places.
  • the gaps located thereat are inflated or expanded into channels whereby a corresponding shaping tool assures a defined pneumatic channel enlargement.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
US06/436,937 1981-10-31 1982-10-27 Heat-exchanger with a bundle of parallelly extending pipes adapted to be acted upon by air Expired - Fee Related US4520863A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3143334 1981-10-31
DE19813143334 DE3143334A1 (de) 1981-10-31 1981-10-31 Waermetauscher mit einem luftbeaufschlagbaren buendel parallel verlaufender rohre

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US (1) US4520863A (fr)
JP (1) JPS5883186A (fr)
DE (1) DE3143334A1 (fr)
FR (1) FR2515804B1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4830100A (en) * 1985-11-25 1989-05-16 The Nippon Aluminium Mfg. Co., Ltd. Heat-pipe device and heat-sink device
US4976309A (en) * 1988-03-04 1990-12-11 Zaporozhsky Avtomobilny ZaVod "Kommunar" (Proizvodstvennoe Objedinenie "AV to ZAZ" Air conditioner for a vehicle
US5947111A (en) * 1998-04-30 1999-09-07 Hudson Products Corporation Apparatus for the controlled heating of process fluids
EP2453515A1 (fr) * 2010-11-10 2012-05-16 Valeo Systèmes Thermiques Dispositif de refroidissement de véhicule, ensemble de refroidissement de batterie de commande de véhicule et procédé de fabrication d'un dispositif de refroidissement de véhicule
US20150027669A1 (en) * 2013-07-26 2015-01-29 Hamilton Sundstrand Corporation Heat exchanger with embedded heat pipes
US20160131441A1 (en) * 2014-11-11 2016-05-12 Northrop Grumman Systems Corporation Alternating channel heat exchanger

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3223496C2 (de) * 1982-06-24 1985-08-08 Daimler-Benz Ag, 7000 Stuttgart Durch eine Gehäusewandung hindurchgeführtes Wärmerohr
AT397575B (de) * 1987-09-24 1994-05-25 Vaillant Gmbh Plattenförmiger wärmetauscher
DE10157446A1 (de) * 2001-11-23 2003-06-12 Webasto Thermosysteme Gmbh Zuheizer für eine Fahrzeug-Klimaanlage mit mindestens einem Wärmerohr
DE10203574A1 (de) * 2002-01-30 2003-08-07 Webasto Thermosysteme Gmbh Heizvorrichtung für ein Personenfahrzeug
JP4919833B2 (ja) * 2007-02-26 2012-04-18 日本オプネクスト株式会社 光電変換モジュール

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3603379A (en) * 1969-04-08 1971-09-07 Carrier Corp Heating and cooling system
US3809154A (en) * 1970-09-21 1974-05-07 Energiagazdalkodasi Intezet Heat exchanger for transferring heat between gases
US3981354A (en) * 1975-03-28 1976-09-21 Curtiss-Wright Corporation Built-up tube and tubesheet assembly for multi-conduit heat exchangers
DE2631092A1 (de) * 1976-07-10 1978-01-12 Rosenthal Technik Ag Keramischer wechselschicht- waermetauscher in modulbauweise
US4333520A (en) * 1979-06-04 1982-06-08 Hitachi, Ltd. Heating and cooling ventilating system with heat recovery

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
DE8012872U1 (de) * 1981-01-22 Koch, William, Ing.(Grad.), 5860 Iserlohn Wärmetauscher
DE1282037B (de) * 1959-05-21 1968-11-07 Julius & August Erbsloeh Komma Blaehkanal-Waermetauscher
JPS5120149A (ja) * 1974-08-09 1976-02-18 Sanyo Electric Co Netsukokansochi
DE2756119A1 (de) * 1977-12-16 1979-06-21 Daimler Benz Ag System zum temperieren eines fahrgastraumes eines kraftfahrzeuges
DE2800265A1 (de) * 1978-01-04 1979-07-12 Daimler Benz Ag System zum temperieren eines fahrgast- oder nutzraumes eines kraftfahrzeuges
DE2834838A1 (de) * 1978-08-09 1980-02-21 Daimler Benz Ag Waermeuebertragung nach dem prinzip des waermerohres
DE2851316A1 (de) * 1978-11-27 1980-05-29 Balcke Duerr Ag Element zum direkten und/oder indirekten waermeaustausch zwischen fluiden
DE3031624C2 (de) * 1980-08-22 1986-04-17 Daimler-Benz Ag, 7000 Stuttgart Wärmerohranordnung zum Temperieren eines Fahrgast- oder Nutzraumes eines brennkraftgetriebenen Fahrzeuges

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3603379A (en) * 1969-04-08 1971-09-07 Carrier Corp Heating and cooling system
US3809154A (en) * 1970-09-21 1974-05-07 Energiagazdalkodasi Intezet Heat exchanger for transferring heat between gases
US3981354A (en) * 1975-03-28 1976-09-21 Curtiss-Wright Corporation Built-up tube and tubesheet assembly for multi-conduit heat exchangers
DE2631092A1 (de) * 1976-07-10 1978-01-12 Rosenthal Technik Ag Keramischer wechselschicht- waermetauscher in modulbauweise
US4333520A (en) * 1979-06-04 1982-06-08 Hitachi, Ltd. Heating and cooling ventilating system with heat recovery

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4830100A (en) * 1985-11-25 1989-05-16 The Nippon Aluminium Mfg. Co., Ltd. Heat-pipe device and heat-sink device
US4976309A (en) * 1988-03-04 1990-12-11 Zaporozhsky Avtomobilny ZaVod "Kommunar" (Proizvodstvennoe Objedinenie "AV to ZAZ" Air conditioner for a vehicle
US5947111A (en) * 1998-04-30 1999-09-07 Hudson Products Corporation Apparatus for the controlled heating of process fluids
EP2453515A1 (fr) * 2010-11-10 2012-05-16 Valeo Systèmes Thermiques Dispositif de refroidissement de véhicule, ensemble de refroidissement de batterie de commande de véhicule et procédé de fabrication d'un dispositif de refroidissement de véhicule
EP3026753A1 (fr) * 2010-11-10 2016-06-01 Valeo Systemes Thermiques Dispositif de refroidissement de véhicule, ensemble de refroidissement de batterie de commande de véhicule et procédé de fabrication d'un dispositif de refroidissement de véhicule
US20150027669A1 (en) * 2013-07-26 2015-01-29 Hamilton Sundstrand Corporation Heat exchanger with embedded heat pipes
US9863716B2 (en) * 2013-07-26 2018-01-09 Hamilton Sundstrand Corporation Heat exchanger with embedded heat pipes
US10473408B2 (en) 2013-07-26 2019-11-12 Hamilton Sundstrand Corporation Heat exchanger with embedded heat pipes
US20160131441A1 (en) * 2014-11-11 2016-05-12 Northrop Grumman Systems Corporation Alternating channel heat exchanger
US9657999B2 (en) * 2014-11-11 2017-05-23 Northrop Grumman Systems Corporation Alternating channel heat exchanger

Also Published As

Publication number Publication date
FR2515804B1 (fr) 1986-04-11
DE3143334C2 (fr) 1987-07-30
FR2515804A1 (fr) 1983-05-06
JPS5883186A (ja) 1983-05-18
DE3143334A1 (de) 1983-05-11

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